[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

US4889039A - Gas compressor with labyrinth sealing and active magnetic bearings - Google Patents

Gas compressor with labyrinth sealing and active magnetic bearings Download PDF

Info

Publication number
US4889039A
US4889039A US07/258,643 US25864388A US4889039A US 4889039 A US4889039 A US 4889039A US 25864388 A US25864388 A US 25864388A US 4889039 A US4889039 A US 4889039A
Authority
US
United States
Prior art keywords
rod
piston
yoke
gas compressor
aperture
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US07/258,643
Inventor
Bernard F. Miller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dresser Rand Co
Original Assignee
Dresser Rand Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Dresser Rand Co filed Critical Dresser Rand Co
Priority to US07/258,643 priority Critical patent/US4889039A/en
Assigned to DRESSER-RAND COMPANY, A GENERAL PARTNERSHIP OF NY reassignment DRESSER-RAND COMPANY, A GENERAL PARTNERSHIP OF NY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: MILLER, BERNARD F.
Application granted granted Critical
Publication of US4889039A publication Critical patent/US4889039A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/047—Details of housings; Mounting of active magnetic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/045—Labyrinth-sealing between piston and cylinder

Definitions

  • This invention pertains to gas compressors, and in particular to a high-pressure, non-lubricated, reciprocating gas compressor in which the relatively moving components thereof are non-contacting.
  • labyrinth-type sealing means in lieu of piston rings or packing rings, and the like. But the efficiency thereof is limited unless it is possible to maintain a piston, and piston rod, in their true centroid positions. If this can be done, then labyrinth sealing for the piston and rod can be held to very minute clearances, will be extremely efficient, and provide non-contacting, i.e., essentially non-wearing, operating components.
  • This will eliminate wear, and allow significant increase in the speed of the compressor.
  • the resulting increase in speed will improve sealing, increase efficiency, and eliminate size problems by allowing much smaller pistons, and shorter strokes, for a given capacity. Wear can be essentially eliminated in normal operation, and heat will be reduced to only the heat of compression.
  • a gas compressor of the reciprocating-piston type, comprising a cylinder having an inner, bore surface; and a piston, reciprocably disposed in said cylinder; wherein said piston has an outer, cylindrical surface; one of said surfaces has means, cooperative with the other of said surfaces, for creating a gas sealing, annular, air dam between said surfaces; said piston has a rod extending therefrom; said cylinder has a closure or wall, at an end thereof, with an aperture formed therein and centrally thereof; said rod is in penetration of said aperture; and further including means interpositioned between said rod and said aperture for suspending said rod, non-contactingly, in said aperture.
  • FIG. 1 is a cross-sectional view, taken along the translating axis of an embodiment of the invention in the form of a single-acting piston arrangement;
  • FIG. 2 is an illustration like that of FIG. 1, but of an alternative embodiment of the invention in the form of a double-acting piston arrangement.
  • FIG. 3 is a cross-sectional view of a scotch-yoke drive mechanism, for use with either the embodiment of FIG. 1 or 2, comprising a further aspect of the invention, the same having been taken, generally, along section 3--3 of FIG. 4; and
  • FIG. 4 is a cross-sectional view taken, generally, along section 4--4 of FIG. 3.
  • FIG. 1 illustrates a typical "single acting" piston compressor 10 with a piston rod 12, projecting from one end, which is connected to a drive mechanism subsequently to be described in connection with FIGS. 3 and 4.
  • This illustration shows an air cooled compressor cylinder 14, but, clearly, it could alternatively be water cooled.
  • Contained with the cylinder 14 is a piston 16 having a multiplicity of convoluted grooves 18 on the outside surface thereof.
  • gas is introduced through a suction valve 20 which allows the gas to be compressed in the compartment 22 and discharged through the valve 24.
  • One end of cylinder 14 is sealed by a head 26 fixed by bolts 28.
  • the other end of the cylinder 14 is closed by a head 30 having an aperture 32, a recess 34, and shoulders 36 formed therein.
  • Convoluted fins 37 are formed on cylinder 14 to allow a dissipation of heat generated by compression of gas.
  • the piston grooves 18 form a labyrinth-type seal as the piston 16 reciprocates, and a pressure drop occurs creating minimal leakage past the piston 16 because of its close fit in the cylinder 14.
  • the close fit is maintained by active, magnetic bearings 38 set in the shoulders 36.
  • Remote, electrical control 40 monitors the bearings-to-rod interface to position the rod 12 and piston 16 extremely close to their respective, true centers within the bore of the cylinder 14 and the aperture 32; they are maintained in this position during piston reciprocation, regardless of external, lateral forces on the piston 16 and/or rod 12.
  • magnetic bearings are those known components which are designed to suspend a moving element, such as a piston, with a minute clearance thereabout within a fixed structure, such as a cylinder.
  • An active magnetic bearing is the known component which is responsive, through control circuitry, to lateral deviations or displacements of the moving element (due to given forces), to cause the element to return to its optimum positioning spaced from (i.e., centrally in) the wall or bore of the host structure.
  • active magnetic bearings are disclosed and discussed, for instance, in U.S. Pat. No. 3,371,984, issued to H.
  • the recess 34 nests an insert 42 of cylindrical configuration having a bore formed with a multiplicity of grooves 44.
  • the latter function like grooves 18 to create an air dam around the rod 12 to seal the rod-to-insert interfacing space against gas leakage therealong.
  • FIG. 2 An alternative version of the invention, in FIG. 2, shows a "double acting" cylinder 14a with compression chambers 22a and 22b, and suction and discharge valves 20a, 20b, 24a and 24b at opposite ends. Also shown are the piston 16a and rods 12a and 12b at both ends. All other structures in FIG. 2, which bear same or similar index numbers as structures in FIG. 1, are the same or similar, in purpose and/or function, as those in FIG. 1.
  • drive mechanism such as a slider crank, wobble or swash plate, scotch yoke or cam/eccentric operation.
  • FIG. 3 and 4 depict a scotch-yoke type of drive mechanism which, in a further aspect of the invention, teaches a novel employment of the active magnetic bearings.
  • a drive shaft 46 has an offset crank pin 48 about which is mounted an active magnetic bearing 38a.
  • the pin 48 and bearing 38a in response to rotation of the shaft 46, travel, with a floating member 49, through the yoke 50, there being another active magnetic bearing 38b between member 49 and yoke 50.
  • the bearing 38a maintains a fine clearance between it and the walls of the member 49
  • bearing 38b maintains a fine clearance between the member 49 and the walls of the yoke 50.
  • the bearing 38a (pin 48, and member 49, of course) translate the yoke 50, but never contact it.
  • the yoke 50 is coupled, at 52, to the rod 12 (which corresponds to the rod 12 in FIG. 1).
  • Shaft 46 has a circular land 54 which receives thereabout another active magnetic bearing 38c.
  • the latter is set within a recess 56 provided therefor in a housing 58, and maintains the land in a minutely spaced, non-contacting disposition relative to the recess 56.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Abstract

The invention, a high-pressure, reciprocating, gas compressor, employs labyrinths to create gas sealing, annular, air dams between the piston and cylinder bore, and piston rod and an aperture in an end wall or closure of the cylinder through which the rod translates, and active magnetic bearings to maintain the piston and rod at their centroids, equally and minutely spaced, fully thereabout, within the bore and aperture. Too, the drive mechanism, a scotch yoke arrangement, has further, active magnetic bearings, to centralize a drive shaft in its housing, and to effect a non-contacting travel of the drive shaft's offset crank, which translates the piston rod, within the yoke.

Description

This invention pertains to gas compressors, and in particular to a high-pressure, non-lubricated, reciprocating gas compressor in which the relatively moving components thereof are non-contacting.
State of the art reciprocating compressors commonly depend on mechanical devices for the sealing of gas pressures between a piston and compression cylinder bore, and between a piston rod and a cylinder end wall or closure, such as piston rings or packing rings. These devices have a very short life, due to rubbing friction, especially at higher pressures. The wear rate is even greater if the compressor has no oil, water, or similar lubrication. Therefore, it has been necessary for the speed of the reciprocating piston to be restricted, to reduce heat and the resulting wear. Restricted speed, in turn, reduces the output capacity of any given compressor. Excessive clearances, caused by frictional heat, and the heat of compression, cause excessive leakage and poor efficiency. Too, noise is generated in the cylinder due to the "kick" or "piston slap" of the piston and rod assembly as it changes direction.
Now, it is well known to employ labyrinth-type sealing means, in lieu of piston rings or packing rings, and the like. But the efficiency thereof is limited unless it is possible to maintain a piston, and piston rod, in their true centroid positions. If this can be done, then labyrinth sealing for the piston and rod can be held to very minute clearances, will be extremely efficient, and provide non-contacting, i.e., essentially non-wearing, operating components.
It is an object of this invention to show that state of the art, active, magnetic bearings can be used to position a piston and rod at their centroids equidistant from the cylinder bore and end wall aperture and, thus, allow a very closely-fitted piston, with convoluted grooves, to form a labyrinth seal with the bore, to form an air dam, and seal gases at pressures up to very high levels, without any contact between the two parts. This will eliminate wear, and allow significant increase in the speed of the compressor. The resulting increase in speed will improve sealing, increase efficiency, and eliminate size problems by allowing much smaller pistons, and shorter strokes, for a given capacity. Wear can be essentially eliminated in normal operation, and heat will be reduced to only the heat of compression. Noise will be reduced too, by eliminating the "piston slap and chucking" action of mechanical seal devices. Too, less parts will be required. The invention will also show that rods can be sealed in the same manner, with convolutes in the bore or aperture in which it translates, or in the rod, with centroid positioning thereof by means of active magnetic bearings.
It is particularly an object of this invention to set forth a gas compressor, of the reciprocating-piston type, comprising a cylinder having an inner, bore surface; and a piston, reciprocably disposed in said cylinder; wherein said piston has an outer, cylindrical surface; one of said surfaces has means, cooperative with the other of said surfaces, for creating a gas sealing, annular, air dam between said surfaces; said piston has a rod extending therefrom; said cylinder has a closure or wall, at an end thereof, with an aperture formed therein and centrally thereof; said rod is in penetration of said aperture; and further including means interpositioned between said rod and said aperture for suspending said rod, non-contactingly, in said aperture. Further objects of this invention, as well as the novel features thereof, will become more apparent by reference to the following description, taken in conjunction with the accompanying figures, in which:
FIG. 1 is a cross-sectional view, taken along the translating axis of an embodiment of the invention in the form of a single-acting piston arrangement;
FIG. 2 is an illustration like that of FIG. 1, but of an alternative embodiment of the invention in the form of a double-acting piston arrangement.
FIG. 3 is a cross-sectional view of a scotch-yoke drive mechanism, for use with either the embodiment of FIG. 1 or 2, comprising a further aspect of the invention, the same having been taken, generally, along section 3--3 of FIG. 4; and
FIG. 4 is a cross-sectional view taken, generally, along section 4--4 of FIG. 3.
FIG. 1 illustrates a typical "single acting" piston compressor 10 with a piston rod 12, projecting from one end, which is connected to a drive mechanism subsequently to be described in connection with FIGS. 3 and 4. This illustration shows an air cooled compressor cylinder 14, but, clearly, it could alternatively be water cooled. Contained with the cylinder 14 is a piston 16 having a multiplicity of convoluted grooves 18 on the outside surface thereof. When driven by a mechanism, in a reciprocating manner, gas is introduced through a suction valve 20 which allows the gas to be compressed in the compartment 22 and discharged through the valve 24. One end of cylinder 14 is sealed by a head 26 fixed by bolts 28. The other end of the cylinder 14 is closed by a head 30 having an aperture 32, a recess 34, and shoulders 36 formed therein. Convoluted fins 37 are formed on cylinder 14 to allow a dissipation of heat generated by compression of gas. The piston grooves 18 form a labyrinth-type seal as the piston 16 reciprocates, and a pressure drop occurs creating minimal leakage past the piston 16 because of its close fit in the cylinder 14. The close fit is maintained by active, magnetic bearings 38 set in the shoulders 36. Remote, electrical control 40 monitors the bearings-to-rod interface to position the rod 12 and piston 16 extremely close to their respective, true centers within the bore of the cylinder 14 and the aperture 32; they are maintained in this position during piston reciprocation, regardless of external, lateral forces on the piston 16 and/or rod 12.
By way of definition, magnetic bearings are those known components which are designed to suspend a moving element, such as a piston, with a minute clearance thereabout within a fixed structure, such as a cylinder. An active magnetic bearing is the known component which is responsive, through control circuitry, to lateral deviations or displacements of the moving element (due to given forces), to cause the element to return to its optimum positioning spaced from (i.e., centrally in) the wall or bore of the host structure. Such active magnetic bearings are disclosed and discussed, for instance, in U.S. Pat. No. 3,371,984, issued to H. Habermann, on May 8, 1973, for a "Magnetic Bearing Block Device for Supporting a Vertical Shaft Adapted for Rotating at High Speed"; NASA Tech Briefs, Summer, 1981, "Magnetic Bearing with Active Control"; and the published brochure: "Actidyne; Application of Active Magnetic Bearings to Industrial Rotating Machinery", Societe de Mecanique Magnetique. The teachings in the aforesaid literature are incorporated herein by reference, and define the nature of the control 40 and bearings 38 arrangement. Control 40 responds to unwanted lateral displacements of the rod 12 and piston 16, relative to the aperture 32 and cylinder bore, respectively, to return the same to optimum, centroid positioning.
The recess 34 nests an insert 42 of cylindrical configuration having a bore formed with a multiplicity of grooves 44. The latter function like grooves 18 to create an air dam around the rod 12 to seal the rod-to-insert interfacing space against gas leakage therealong.
An alternative version of the invention, in FIG. 2, shows a "double acting" cylinder 14a with compression chambers 22a and 22b, and suction and discharge valves 20a, 20b, 24a and 24b at opposite ends. Also shown are the piston 16a and rods 12a and 12b at both ends. All other structures in FIG. 2, which bear same or similar index numbers as structures in FIG. 1, are the same or similar, in purpose and/or function, as those in FIG. 1.
Most any, commonly-known type of drive mechanism can be used, such as a slider crank, wobble or swash plate, scotch yoke or cam/eccentric operation.
FIG. 3 and 4 depict a scotch-yoke type of drive mechanism which, in a further aspect of the invention, teaches a novel employment of the active magnetic bearings.
A drive shaft 46 has an offset crank pin 48 about which is mounted an active magnetic bearing 38a. The pin 48 and bearing 38a, in response to rotation of the shaft 46, travel, with a floating member 49, through the yoke 50, there being another active magnetic bearing 38b between member 49 and yoke 50. With the travel, the bearing 38a maintains a fine clearance between it and the walls of the member 49, and bearing 38b maintains a fine clearance between the member 49 and the walls of the yoke 50. Hence, the bearing 38a (pin 48, and member 49, of course) translate the yoke 50, but never contact it. The yoke 50 is coupled, at 52, to the rod 12 (which corresponds to the rod 12 in FIG. 1).
Shaft 46 has a circular land 54 which receives thereabout another active magnetic bearing 38c. The latter is set within a recess 56 provided therefor in a housing 58, and maintains the land in a minutely spaced, non-contacting disposition relative to the recess 56.
While I have described my invention in connection with specific embodiments thereof, it is to be clearly understood that this is done only by way of example, and not as a limitation of the scope of the invention as set forth in the objects thereof and in the appended claims.

Claims (8)

I claim:
1. A gas compressor, of the reciprocating-piston type, comprising:
a cylinder having an inner, bore surface; and
a piston, reciprocally disposed in said cylinder; wherein
said piston has an outer, cylindrical surface;
one of said surfaces has means, cooperative with the other of said surfaces, for creating a gas sealing, annular, air dam between said surfaces;
said piston has a rod extending therefrom;
said cylinder has a closure or wall at an end thereof, with an aperture formed therein and centrally thereof;
said rod is in penetration of said aperture; and further including
means interpositioned between said rod and said aperture for suspending said rod noncontactingly in said aperture;
a rotary drive shaft having an offset crank pin;
a yoke circumjacent said pin;
means coupling said yoke to said rod;
an active magnetic bearing interpositioned between said yoke and said pin;
a floating member (a) confined within said yoke, and (b) circumjacent said pin, being interpositioned between said pin and said yoke;
a second active magnetic bearing interpositioned between said member and said yoke; wherein
said pin causes said member to translate, within said yoke, transverse to said rod; and
said bearings noncontactingly suspend (a) said pin in said member, and (b) said member in said yoke.
2. A gas compressor, according to claim 1, wherein:
said air dam creating means comprises a labyrinth.
3. A gas compressor, according to claim 1, wherein:
said rod and said aperture have mutually complementary, surfaces; and
one of said complementary surfaces has means; cooperative with the other thereof, for creating another, gas sealing, annular air dam therebetween.
4. A gas compressor, according to claim 3, wherein:
said another air dam creating means comprises a labyrinth.
5. A gas compressor, according to claim 3, wherein:
said aperture has a multiplicity of annular grooves formed therein.
6. A gas compressor, according to claim 1, wherein:
said rod suspending means comprises an active magnetic bearing.
7. A gas compressor according to claim 1, wherein:
said rod suspending means comprises a pair of active magnetic bearings, set in said closure or wall, in spaced apart disposition.
8. A gas compressor, according to claim 1, wherein:
said outer, cylindrical surface of said piston has a multiplicity of annular grooves formed therein.
US07/258,643 1988-10-17 1988-10-17 Gas compressor with labyrinth sealing and active magnetic bearings Expired - Lifetime US4889039A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US07/258,643 US4889039A (en) 1988-10-17 1988-10-17 Gas compressor with labyrinth sealing and active magnetic bearings

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US07/258,643 US4889039A (en) 1988-10-17 1988-10-17 Gas compressor with labyrinth sealing and active magnetic bearings

Publications (1)

Publication Number Publication Date
US4889039A true US4889039A (en) 1989-12-26

Family

ID=22981488

Family Applications (1)

Application Number Title Priority Date Filing Date
US07/258,643 Expired - Lifetime US4889039A (en) 1988-10-17 1988-10-17 Gas compressor with labyrinth sealing and active magnetic bearings

Country Status (1)

Country Link
US (1) US4889039A (en)

Cited By (43)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5050895A (en) * 1989-04-04 1991-09-24 Flow International Corporation High pressure dynamic seal
US5216308A (en) * 1989-05-25 1993-06-01 Avcon-Advanced Controls Technology, Inc. Magnetic bearing structure providing radial, axial and moment load bearing support for a rotatable shaft
US5218896A (en) * 1986-11-06 1993-06-15 Canon Kabushiki Kaisha Driving mechanism with gas bearing
US5250865A (en) * 1992-04-30 1993-10-05 Avcon - Advanced Controls Technology, Inc. Electromagnetic thrust bearing for coupling a rotatable member to a stationary member
US5315197A (en) * 1992-04-30 1994-05-24 Avcon - Advance Controls Technology, Inc. Electromagnetic thrust bearing using passive and active magnets, for coupling a rotatable member to a stationary member
US5411366A (en) * 1991-12-04 1995-05-02 Environamics Corporation Motor driven environmentally safe pump
US5499901A (en) * 1994-03-17 1996-03-19 Environamics Corporation Bearing frame clearance seal construction for a pump
US5513964A (en) * 1994-10-11 1996-05-07 Environamics Corporation Pump oil mister with reduced windage
US5514924A (en) * 1992-04-30 1996-05-07 AVCON--Advanced Control Technology, Inc. Magnetic bearing providing radial and axial load support for a shaft
WO1997037132A1 (en) * 1996-03-29 1997-10-09 Xiaoying Yun Rotary pump
US5848879A (en) * 1993-11-18 1998-12-15 Pressmaster Tool Ab Cylinder lining for hydraulic pump
US5924847A (en) * 1997-08-11 1999-07-20 Mainstream Engineering Corp. Magnetic bearing centrifugal refrigeration compressor and refrigerant having minimum specific enthalpy rise
WO2002040843A1 (en) * 2000-11-20 2002-05-23 Jaakko Larjola Two-stroke engine
US6591624B1 (en) * 1995-06-14 2003-07-15 Ullrich Hesse Air conditioning system for an automobile
US20040021108A1 (en) * 2002-07-30 2004-02-05 Siemens-Elema Ab Valve assembly
WO2003006826A3 (en) * 2001-07-13 2004-04-01 Capital Formation Inc Elastomeric sealing element for gas compressor valve
US20040144868A1 (en) * 2003-01-23 2004-07-29 Denso Corporation Sliding structure for shaft member with improved abrasion resistance and injector
US20050123426A1 (en) * 2003-12-03 2005-06-09 Schaake Mark D. Multi-directional pump
US20050280318A1 (en) * 2004-06-17 2005-12-22 Parison James A Self-cooling actuator
US20070210659A1 (en) * 2006-03-07 2007-09-13 Long Johnny D Radial magnetic cam
EP1869322A1 (en) * 2005-03-17 2007-12-26 Fuelmaker Corporation Oil-less compressor with seal-dust protection
WO2009004046A1 (en) * 2007-07-04 2009-01-08 Arcelik Anonim Sirketi A compressor
DE102007061847A1 (en) 2007-12-20 2009-06-25 Stasskol Kolbenstangendichtungen Gmbh Sealing device i.e. labyrinth seal, for sealing article i.e. piston rod of piston compressor, has radial separating cut for dividing seal ring into individual ring segment, where impact tolerance of device is closed in operating condition
WO2011026774A1 (en) * 2009-09-03 2011-03-10 Siemens Aktiengesellschaft Piston engine having magnetic piston bearing
WO2012013462A1 (en) * 2010-07-28 2012-02-02 Robert Bosch Gmbh Piston engine drivable using a steam power process
WO2012013470A1 (en) * 2010-07-28 2012-02-02 Robert Bosch Gmbh Piston engine drivable using a steam power process
WO2012013463A1 (en) * 2010-07-28 2012-02-02 Robert Bosch Gmbh Piston engine drivable using a steam power process
US8656895B2 (en) 2011-12-29 2014-02-25 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
US8720317B2 (en) * 2011-12-29 2014-05-13 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
US8899192B2 (en) 2011-12-29 2014-12-02 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
US9097203B2 (en) 2011-12-29 2015-08-04 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
US9169797B2 (en) 2011-12-29 2015-10-27 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
EP2971645A4 (en) * 2013-03-15 2016-12-28 Prime Group Alliance Llc Opposed piston internal combustion engine with inviscid layer sealing
JP2017089595A (en) * 2015-11-17 2017-05-25 株式会社日本製鋼所 Labyrinth piston type reciprocating compressor
US20170218935A1 (en) * 2014-07-31 2017-08-03 Burckhardt Compression Ag Housing upper part of a labyrinth piston compressor and method for cooling same, and labyrinth piston compressor
US10215229B2 (en) 2013-03-14 2019-02-26 Etagen, Inc. Mechanism for maintaining a clearance gap
US20190178237A1 (en) * 2016-09-12 2019-06-13 Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai Linear compressor
US20210025378A1 (en) * 2019-06-25 2021-01-28 Beijing Beifen-Ruili Analytical Instrument (Group) Co., Ltd. Piston seal structure for injector
US10985641B2 (en) 2018-07-24 2021-04-20 Mainspring Energy, Inc. Linear electromagnetic machine system with bearing housings having pressurized gas
WO2021078781A1 (en) * 2019-10-21 2021-04-29 Burckhardt Compression Ag Piston compressor and method for operating same
WO2021228598A1 (en) * 2020-05-11 2021-11-18 OET GmbH Reciprocating compressor for generating oil-free compressed air
US20210404454A1 (en) * 2018-09-24 2021-12-30 Burckhardt Compression Ag Labyrinth piston compressor
IT202200000263A1 (en) * 2022-01-11 2023-07-11 Nuovo Pignone Tecnologie Srl Magnetic Bearing for supporting an RC Piston

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US17855A (en) * 1857-07-21 of same place
US2878990A (en) * 1953-10-30 1959-03-24 Sulzer Ag Upright piston compressor
US3422765A (en) * 1967-03-24 1969-01-21 Gen Electric Superconducting liquid helium pump
DE1403763A1 (en) * 1961-03-02 1969-01-30 Endres Dr Ing Johann Piston without seal ring with central guide
US3731984A (en) * 1970-10-22 1973-05-08 H Habermann Magnetic bearing block device for supporting a vertical shaft adapted for rotating at high speed
US4304410A (en) * 1979-09-20 1981-12-08 Kobe, Inc. Sealing structure for reciprocating pistons exposed to high pressure differentials
US4389849A (en) * 1981-10-02 1983-06-28 Beggs James M Administrator Of Stirling cycle cryogenic cooler
US4627795A (en) * 1982-03-30 1986-12-09 Linde Aktiengesellschaft Piston assembly for a compressor or the like

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US17855A (en) * 1857-07-21 of same place
US2878990A (en) * 1953-10-30 1959-03-24 Sulzer Ag Upright piston compressor
DE1403763A1 (en) * 1961-03-02 1969-01-30 Endres Dr Ing Johann Piston without seal ring with central guide
US3422765A (en) * 1967-03-24 1969-01-21 Gen Electric Superconducting liquid helium pump
US3731984A (en) * 1970-10-22 1973-05-08 H Habermann Magnetic bearing block device for supporting a vertical shaft adapted for rotating at high speed
US4304410A (en) * 1979-09-20 1981-12-08 Kobe, Inc. Sealing structure for reciprocating pistons exposed to high pressure differentials
US4389849A (en) * 1981-10-02 1983-06-28 Beggs James M Administrator Of Stirling cycle cryogenic cooler
US4627795A (en) * 1982-03-30 1986-12-09 Linde Aktiengesellschaft Piston assembly for a compressor or the like

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
NASA, Magnetic Bearing with Active Control, 9/1981. *
Soci t de M canique Magn tique, Actidyne, Application of Active Magnetic Bearings to Industrial Rotating Machinery. *
Societe de Mecanique Magnetique, Actidyne, Application of Active Magnetic Bearings to Industrial Rotating Machinery.

Cited By (70)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5218896A (en) * 1986-11-06 1993-06-15 Canon Kabushiki Kaisha Driving mechanism with gas bearing
US5050895A (en) * 1989-04-04 1991-09-24 Flow International Corporation High pressure dynamic seal
US5216308A (en) * 1989-05-25 1993-06-01 Avcon-Advanced Controls Technology, Inc. Magnetic bearing structure providing radial, axial and moment load bearing support for a rotatable shaft
US5411366A (en) * 1991-12-04 1995-05-02 Environamics Corporation Motor driven environmentally safe pump
US5499902A (en) * 1991-12-04 1996-03-19 Environamics Corporation Environmentally safe pump including seal
US5514924A (en) * 1992-04-30 1996-05-07 AVCON--Advanced Control Technology, Inc. Magnetic bearing providing radial and axial load support for a shaft
US5250865A (en) * 1992-04-30 1993-10-05 Avcon - Advanced Controls Technology, Inc. Electromagnetic thrust bearing for coupling a rotatable member to a stationary member
US5315197A (en) * 1992-04-30 1994-05-24 Avcon - Advance Controls Technology, Inc. Electromagnetic thrust bearing using passive and active magnets, for coupling a rotatable member to a stationary member
US5848879A (en) * 1993-11-18 1998-12-15 Pressmaster Tool Ab Cylinder lining for hydraulic pump
US5499901A (en) * 1994-03-17 1996-03-19 Environamics Corporation Bearing frame clearance seal construction for a pump
US5513964A (en) * 1994-10-11 1996-05-07 Environamics Corporation Pump oil mister with reduced windage
US5632608A (en) * 1994-10-11 1997-05-27 Environamics Corporation Pump oil mister with reduced windage
US6591624B1 (en) * 1995-06-14 2003-07-15 Ullrich Hesse Air conditioning system for an automobile
WO1997037132A1 (en) * 1996-03-29 1997-10-09 Xiaoying Yun Rotary pump
US5924847A (en) * 1997-08-11 1999-07-20 Mainstream Engineering Corp. Magnetic bearing centrifugal refrigeration compressor and refrigerant having minimum specific enthalpy rise
WO2002040843A1 (en) * 2000-11-20 2002-05-23 Jaakko Larjola Two-stroke engine
WO2003006826A3 (en) * 2001-07-13 2004-04-01 Capital Formation Inc Elastomeric sealing element for gas compressor valve
US20040021108A1 (en) * 2002-07-30 2004-02-05 Siemens-Elema Ab Valve assembly
US6886801B2 (en) * 2002-07-30 2005-05-03 Maquet Critical Care Ab Valve assembly
US7118046B2 (en) * 2003-01-23 2006-10-10 Denso Corporation Sliding structure for shaft member with improved abrasion resistance and injector
US20040144868A1 (en) * 2003-01-23 2004-07-29 Denso Corporation Sliding structure for shaft member with improved abrasion resistance and injector
US7329105B2 (en) 2003-12-03 2008-02-12 Haldex Brake Corporation Multi-directional pump
US20050123426A1 (en) * 2003-12-03 2005-06-09 Schaake Mark D. Multi-directional pump
US20050280318A1 (en) * 2004-06-17 2005-12-22 Parison James A Self-cooling actuator
US7202577B2 (en) * 2004-06-17 2007-04-10 Bose Corporation Self-cooling actuator
EP1869322A1 (en) * 2005-03-17 2007-12-26 Fuelmaker Corporation Oil-less compressor with seal-dust protection
EP1869322A4 (en) * 2005-03-17 2009-11-11 Fuelmaker Corp Oil-less compressor with seal-dust protection
US20070210659A1 (en) * 2006-03-07 2007-09-13 Long Johnny D Radial magnetic cam
WO2009004046A1 (en) * 2007-07-04 2009-01-08 Arcelik Anonim Sirketi A compressor
DE102007061847A1 (en) 2007-12-20 2009-06-25 Stasskol Kolbenstangendichtungen Gmbh Sealing device i.e. labyrinth seal, for sealing article i.e. piston rod of piston compressor, has radial separating cut for dividing seal ring into individual ring segment, where impact tolerance of device is closed in operating condition
WO2011026774A1 (en) * 2009-09-03 2011-03-10 Siemens Aktiengesellschaft Piston engine having magnetic piston bearing
US8978595B2 (en) 2009-09-03 2015-03-17 Siemens Aktiengesellschaft Piston engine having magnetic piston bearing
CN102482994B (en) * 2009-09-03 2014-07-09 西门子公司 Piston engine having magnetic piston bearing
CN102482994A (en) * 2009-09-03 2012-05-30 西门子公司 Piston engine having magnetic piston bearing
WO2012013463A1 (en) * 2010-07-28 2012-02-02 Robert Bosch Gmbh Piston engine drivable using a steam power process
WO2012013470A1 (en) * 2010-07-28 2012-02-02 Robert Bosch Gmbh Piston engine drivable using a steam power process
CN103026002A (en) * 2010-07-28 2013-04-03 罗伯特·博世有限公司 Piston engine drivable using a steam power process
WO2012013462A1 (en) * 2010-07-28 2012-02-02 Robert Bosch Gmbh Piston engine drivable using a steam power process
US9097203B2 (en) 2011-12-29 2015-08-04 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
US10006401B2 (en) 2011-12-29 2018-06-26 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
US8899192B2 (en) 2011-12-29 2014-12-02 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
US8720317B2 (en) * 2011-12-29 2014-05-13 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
US9004038B2 (en) 2011-12-29 2015-04-14 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
USRE49259E1 (en) 2011-12-29 2022-10-25 Mainspring Energy, Inc. Methods and systems for managing a clearance gap in a piston engine
US9169797B2 (en) 2011-12-29 2015-10-27 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
US8656895B2 (en) 2011-12-29 2014-02-25 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
US8770090B2 (en) 2011-12-29 2014-07-08 Etagen, Inc. Methods and systems for managing a clearance gap in a piston engine
US10215229B2 (en) 2013-03-14 2019-02-26 Etagen, Inc. Mechanism for maintaining a clearance gap
AU2014233020B2 (en) * 2013-03-15 2018-07-12 Prime Group Alliance, Llc Opposed piston internal combustion engine with inviscid layer sealing
EP2971645A4 (en) * 2013-03-15 2016-12-28 Prime Group Alliance Llc Opposed piston internal combustion engine with inviscid layer sealing
JP2020012468A (en) * 2013-03-15 2020-01-23 プライム グループ アライアンス, リミテッド ライアビリティ カンパニーPrime Group Alliance, LLC Opposed piston internal combustion engine with non-viscous layer sealing
US20170218935A1 (en) * 2014-07-31 2017-08-03 Burckhardt Compression Ag Housing upper part of a labyrinth piston compressor and method for cooling same, and labyrinth piston compressor
JP2017089595A (en) * 2015-11-17 2017-05-25 株式会社日本製鋼所 Labyrinth piston type reciprocating compressor
US20190178237A1 (en) * 2016-09-12 2019-06-13 Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai Linear compressor
US10876524B2 (en) * 2016-09-12 2020-12-29 Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai Linear compressor
US10985641B2 (en) 2018-07-24 2021-04-20 Mainspring Energy, Inc. Linear electromagnetic machine system with bearing housings having pressurized gas
US11616428B2 (en) 2018-07-24 2023-03-28 Mainspring Energy, Inc. Linear electromagnetic machine system
US20210404454A1 (en) * 2018-09-24 2021-12-30 Burckhardt Compression Ag Labyrinth piston compressor
US11434889B2 (en) * 2019-06-25 2022-09-06 Beijing Beifen-Ruili Analytical Instrument (Group) Co., Ltd. Piston seal structure for injector
US20210025378A1 (en) * 2019-06-25 2021-01-28 Beijing Beifen-Ruili Analytical Instrument (Group) Co., Ltd. Piston seal structure for injector
CN114787510A (en) * 2019-10-21 2022-07-22 伯克哈特压缩机股份公司 Packing seal for a piston compressor and method for operating the same
CN114829771A (en) * 2019-10-21 2022-07-29 伯克哈特压缩机股份公司 Piston compressor and method for operating the same
WO2021078820A1 (en) * 2019-10-21 2021-04-29 Burckhardt Compression Ag Packing seal for a piston compressor and method for operating same
US20220372962A1 (en) * 2019-10-21 2022-11-24 Burckhardt Compression Ag Packing seal for a piston compressor and method for operating same
US20220372963A1 (en) * 2019-10-21 2022-11-24 Burckhardt Compression Ag Piston compressor and method for operating same
WO2021078781A1 (en) * 2019-10-21 2021-04-29 Burckhardt Compression Ag Piston compressor and method for operating same
JP7564200B2 (en) 2019-10-21 2024-10-08 ブルクハルト コンプレッション アーゲー Packing seal for piston compressor and method for operating piston compressor
WO2021228598A1 (en) * 2020-05-11 2021-11-18 OET GmbH Reciprocating compressor for generating oil-free compressed air
IT202200000263A1 (en) * 2022-01-11 2023-07-11 Nuovo Pignone Tecnologie Srl Magnetic Bearing for supporting an RC Piston
WO2023135027A1 (en) * 2022-01-11 2023-07-20 Nuovo Pignone Tecnologie - S.R.L. Magnetic bearing for supporting an rc piston

Similar Documents

Publication Publication Date Title
US4889039A (en) Gas compressor with labyrinth sealing and active magnetic bearings
EP0942204A1 (en) Piston sealing ring assembly
US9353862B2 (en) Piston for a reciprocating hermetic compressor
US5195320A (en) Piston-cylinder assembly particularly useful in stirling cycle machines
KR930013479A (en) Inclined Plate Compressor
US3954048A (en) High pressure actuator
US3946617A (en) Motion translation mechanism
US5850777A (en) Floating wrist pin coupling for a piston assembly
KR100560584B1 (en) Lip seal wear sleeve
CA1106694A (en) Dual piston pump with pressure seal lubrication feature
EP1426618B1 (en) Lip seal lubrification reservoir and method of level control
US3747478A (en) Liquid sealing means for a high pressure pump
US3120338A (en) Compressor
JPH0743551Y2 (en) Rotary shaft seal device for high pressure fluid
US4080114A (en) Oscillating positive displacement machine
JPH0544549Y2 (en)
EP0386598A1 (en) Fluid operated rotary actuator
JP2020076389A (en) Reciprocation pump
KR100736070B1 (en) Lubricating system for connecting rod of compressor
KR100592440B1 (en) Multi-stage compressor
JPH0529405Y2 (en)
KR100323127B1 (en) A sealing ring device for a reciprocation and compression machinery
GB1577950A (en) Piston compressors
GB2087485A (en) Compressor
JP2023169602A (en) reciprocating compressor

Legal Events

Date Code Title Description
AS Assignment

Owner name: DRESSER-RAND COMPANY, STE. 500 BARON STEUBEN PLACE

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:MILLER, BERNARD F.;REEL/FRAME:004963/0854

Effective date: 19881005

Owner name: DRESSER-RAND COMPANY, A GENERAL PARTNERSHIP OF NY,

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:MILLER, BERNARD F.;REEL/FRAME:004963/0854

Effective date: 19881005

STCF Information on status: patent grant

Free format text: PATENTED CASE

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 4

FPAY Fee payment

Year of fee payment: 8

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

Free format text: PAYER NUMBER DE-ASSIGNED (ORIGINAL EVENT CODE: RMPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 12